DE102011016053B4 - Adjustable fitting with a reduced drive torque - Google Patents

Abstract

Adjustable fitting (10), in particular for motor vehicle seats, in which a fixed fitting part (11) assigned to the seat part and an adjustable fitting part (12) assigned to the backrest have an adjustment and locking device which determines the position of the two fitting parts (11, 12) relative to one another Gears are connected to one another, the fitting parts (11, 12) of which are mounted eccentrically in the effective plane of their toothing (16, 18) under the influence of at least one drive means (22) which can be rotated about a pivot axis (Y), characterized in that at least one drive means (22) with a force transmitted from at least one drive point to wedge segments (24) at at least one effective point (31, 31') in the area of the broad sides of the two wedge segments (24), which is in each case close to a surface (26) of the wedge segments (24) lies, acts in such a way that the wedge segments (24) are reinforced in a direction of force (F31, F31') lying in the circumferential direction of the adjustment fitting (10). are operated, with a spring element (13) which is arranged separately from the drive means (22) and which, as an energy store, pulls the narrow sides of the wedge segments (24) together in the sense of influencing radial play.

Description

The invention relates to an adjustment fitting with the features of the preamble of patent claim 1.

A variety of adjustment fittings is known from the prior art, with only an example DE 30 13 304 C2 and the DE 10 2004 013 272 B3 are named.

The patent specification should serve as the starting point for the invention DE 44 36 101 B4 to serve. This publication describes an adjustment fitting for a seat in which a fixed fitting assigned to the seat part and an adjustable fitting assigned to the backrest are connected to one another via a gear mechanism which determines the position of both fittings and acts as an adjusting and locking device. The locking and locking device has an eccentric means for mounting the two fitting parts in the plane of its toothing, which is formed from two wedge segments that are inclined towards one another and encompass a driver in some areas, a driver arm that grips between their narrow sides and an energy accumulator that presses the broad sides of the wedge segments apart. In this case, the driver is assigned a central receptacle for a non-rotatable connection with a transmission rod. The transmission rod is used to introduce the torque required to adjust the inclination of the backrest into the gear and to transmit the torque to a similar fitting on the other side of the seat. The driver is designed as a cover disk with a hub which has the central torque-transmitting receptacle, the cover disk being integrally connected to the driver arm arranged radially away from the hub, the cover disk overlapping the transmission area on the outside of the fitting part.

For clarification, the adjustment fitting is shown below DE 44 36 101 B4 by means of the 1 explained in more detail.

The adjustment fitting 10, which is arranged on both long seat sides of a vehicle and connects the seat part to the backrest, has a first fitting part 11, which is fixed and connected to the seat part, and a second fitting part 12, which is connected to the backrest and is adjustable relative to the first fitting part 11 Eccentric means 14 comprehensive pivot axis Y are connected to each other, which are part of the designed as a gear adjusting and locking device. This transmission also includes a spur gear 15 formed, for example, by embossing from the second fitting part 12 and having external teeth 16 which mesh with the internal teeth 18 of a ring gear 17 of the first fitting part 11, also formed, for example, by embossing. The diameter of the addendum circle of the external toothing 16 is at least one tooth height smaller than the diameter of the root circle of the internal toothing 18. Accordingly, the toothings 16 and 18 have numbers of teeth that differ by at least one tooth, with the number of teeth of the internal toothing 18 being greater than that Number of teeth of the external toothing 16. The arrangement shown is chosen such that the external toothing 16 can roll on the internal toothing 18.

The first fitting part 11 has, concentrically to its internal teeth 18, a collar 19 in which a driver 20 designed as a bushing is mounted. This carrier 20, which is preferably made of plastic and is mostly formed in one piece, comprises a hub 21, which is rotatably mounted with its outer casing in the collar 19 of the first fitting part 11, with the hub 21 being connected to a carrier arm which overlaps the collar 19 in some areas and is arranged at a radial distance from the hub 21 which in turn, like the hub on the outside of the adjustment fitting 10, merges into a cover disk (not shown) that overlaps the transmission area. In the plane of the driver arm, two wedge segments 24 are supported on the collar 19 with their inner surfaces, which are in contact with their outer surface on a bearing ring 25 fixed in the spur gear 15 of the second fitting part 12 . While the narrow end faces of the wedge segments 24 are located at a small distance from the driver arm when the adjustment fitting 10 is in the locked position, the wide end faces of the wedge segments 24 are acted upon by the spring legs 27 in the manner of an annular spring in the sense of spreading apart. These wedge segments 24 together with the collar 19 of the first fitting part 11 create an eccentric section through which the spur gear 15 is pressed with its toothing 16 into the toothing 18 of the inner ring gear of the first fitting part 11 in extension of the eccentric highest point.

The wedge segments 24 are in the just means 1 described in detail DE 44 36 101 B4 driven on their narrow sides by a driver arm to be regarded as a driving means - in short: "drive means". The end faces of the broad sides of the wedge segments 24 are gripped by an energy accumulator in the manner of an annular spring via the two spring legs 27 and press the wedge segments 24 apart via the broad sides of the wedge segments 24 .

In the above already mentioned DE 30 13 304 C2 the wedge segments are also driven on their narrow sides by a "drive means" in the form of a drive plate. Here, too, the broad sides of the wedge segments are grasped at their end faces by an energy accumulator, here in the form of a helical compression spring, and press the wedge segments apart via the end faces of the broad sides of the wedge segments.

In the one already mentioned above DE 10 2004 013 272 B3 the wedge segments are also driven on their narrow sides by a "drive means", here in the manner of a driver finger, which is arranged on a driver disk of a driver hub, analogously to the publications explained above. The end faces of the broad sides of the wedge segments are gripped by an energy accumulator, this time in the form of an omega spring, and likewise press the wedge segments apart via the end faces of the broad sides of the wedge segments.

The technically basically similarly constructed adjustment fittings from the prior art have in common that the drive surfaces of the drive means act on the narrow sides of the wedge segments and the force accumulator influencing the radial play of the wedge segments acts on the respective broad side of the wedge segments.

In order to keep the drive torque of the adjustment fittings as low as possible, low-friction plain bearings are used in the majority of constructions of the fitting parts that move eccentrically to one another in the manner of bearings. This makes it clear, for example, that the person skilled in the art always orients his considerations towards enabling a reduction in the drive torque of an adjustment fitting.

The object of the invention is to reduce the drive torque of an adjustment fitting.

The invention solves the problem by some features from the document
DE 44 36 101 B4 are known, which describes an adjustment fitting, in particular a backrest adjustment fitting for motor vehicle seats, in which a fixed, first fitting part assigned to the seat part and an adjustable, second fitting part assigned to the backrest are connected to one another via a gear mechanism which determines the position of the two fitting parts relative to one another and acts as an adjusting and locking device are connected, the fittings are mounted eccentrically in the effective plane of their teeth under the influence of at least one rotatable about a pivot axis driving means.

According to the invention, it is provided that at least one drive means, with a force transmitted from at least one drive point to the wedge segments, acts on at least one effective point in the area of the broad sides of the two wedge segments, which is close to a surface of the wedge segments, in such a way that the wedge segments are reinforced in a circumferential direction be driven in the direction of force lying in the adjustment fitting, with a spring element which is arranged separately from the drive means and which, as an energy accumulator, pulls the narrow sides of the wedge segments together in the sense of influencing radial play.

In a first difference to the prior art, the drive means does not act on the narrow sides of the wedge segments, but transmits the force via the broad sides of the two wedge segments. This is advantageous because the drive means—in the manner of a driver—acts directly on the driving wedge segment and the wedge segment that is not directly driven is pulled behind.

Furthermore, in a second difference from the prior art, it is provided that an energy accumulator designed as a spring element does not grasp the broad sides, but rather the narrow sides of the wedge segments and pulls them together in the sense of influencing radial play. This is advantageous because a simple, space-saving design of the spring element is possible.

The design is thus compared to the DE 44 36 101 B4 arranged inverted. In the DE 44 36 101 B4 the drive means, the driver arm, engages on the narrow side and the spring element on the broad side. For this reason, the solution according to the invention speaks of an “inverted driver” or of a driver arranged “inverted” compared to the prior art.

With the adjustment fitting according to the invention, it is ensured that at least one drive means forms at least one active point in the area of the broad sides of the two wedge segments with a force transmitted from at least one drive point to the wedge segments, which is close to the surface of the wedge segments and acts there in such a way that the Wedge segments are driven without friction in the circumferential direction of the adjustment fitting.

In a preferred embodiment of the invention, the points of action to which at least one force is applied by the drive points of the at least one drive means are designed as contours near the surfaces of the wedge segments, which are arranged or formed in the inner surfaces of the wedge segments. It has changed at Mes It has been found that locating the drive points close to the surfaces is beneficial in reducing friction with components adjacent to the wedge segments. The reduction in friction comes about because the drive means—in the manner of the driver—acts directly on the driving wedge segment and the wedge segment that is not directly driven is pulled behind it.

In a further preferred embodiment of the invention, the action points acting on the wedge segments, to which at least one force is applied from the drive points of the at least one drive means, are not only arranged near the surfaces of the wedge segments, but also the drive points formed in the contours of the inner surfaces of the wedge segments and thus the action points of the at least one drive means are arranged as close as possible to the outer surfaces of the wedge segments.

This is advantageous because the direction of force that is transmitted to the wedge segments by the drive means acts on the wedge segments further outwards in the circumferential direction, thereby reducing the frictional force compared to the bearing ring located on the outer surface of the wedge segments in the direction of the force.

In contrast to the prior art, these technical features of the resulting embodiments, which are described in detail below, advantageously result in a reduction in the drive torque, whereby the effort required to adjust an adjustment fitting by the user is reduced or it can possibly be increased at least one expensive plain bearing, which usually consists of expensive materials, can be dispensed with.

In addition, it has been found that in a preferred embodiment of the invention, the use of contours in the driver and in the wedge segments that correspond in terms of their shape is advantageous for the reliable transmission of the high driving forces between the driver and wedge segments and wedge segments and the spring element influencing the radial play in an adjustment fitting .

In a preferred embodiment of the invention, the adjustment fitting forms contours on the drive means side in the wedge segments in the area of the broad sides, near the broad end faces.

In a further development of the preferred embodiment, the contours on the drive means side are inner contours which, together with the outer contours of the drive means which engages in the inner contours and is designed in the manner of a driver, form imaginary active points which function as drive points of the drive means.

In a preferred embodiment of the invention, the inner contours are formed in that the drive points or active points of the drive means are arranged at a definable distance from the adjustment axis of the adjustment fitting, with the distance being determined by adjusting a depth of a depression forming the inner contour in the wedge segments or correspondingly by the Length of an outer contour forming extensions of the drive means is made, which engage in the corresponding depressions.

In a preferred embodiment, the spring element engages with its end regions near the narrow end face of the wedge segments on the left and right in the left and right wedge segment in contours on the spring element side, which are preferably also designed as inner contours.

In a preferred development, the contours on the spring element side are formed in the wedge segments as groove-like indentations, as a result of which the ends of the spring element can advantageously be fastened particularly easily in the indentations, in particular hooked.

Finally, in a preferred embodiment of the invention, it is provided that the driver of the adjustment fitting is designed as a cover disc with a hub that has a central, torque-transmitting receptacle, the cover disc being integrally connected to the driver arranged at a radial distance from the hub, the cover disc Transmission area of the two fitting parts overlaps on the outside.

• 1 einen Verstellbeschlag nach dem Stand der Technik;
• 2 eine schematische Ansicht auf den exzentrischen Lagerbereich des erfindungsgemäßen Verstellbeschlages in einer ersten Ausführungsform, bei der Konturen in den Keilsegmenten ausgebildet sind, wobei das an ihnen angreifende Antriebsmittel Wirkpunkte bildet, die nahe der stirnseitigen Fläche der Keilsegmente und im Wesentlichen nahe einer jeweiligen Innenfläche der Keilsegmente angeordnet sind;
• 3 eine schematische Ansicht auf den exzentrischen Lagerbereich des erfindungsgemäßen Verstellbeschlages in einer zweiten Ausführungsform, bei der Konturen in den Keilsegmenten ausgebildet sind, wobei das an ihnen angreifende Antriebsmittel Wirkpunkte bildet, die den stirnseitigen Flächen der Keilsegmente noch näher und ferner weiter in Richtung einer jeweiligen Außenfläche der Keilsegmente angeordnet sind.

The invention is explained in more detail below in principle in two embodiments with reference to the associated drawings. Show it:

• 1 a prior art adjustment fitting;
• 2 a schematic view of the eccentric bearing area of the adjustment fitting according to the invention in a first embodiment, in which contours are formed in the wedge segments, with the drive means acting on them forming points of action which are arranged near the front surface of the wedge segments and essentially near a respective inner surface of the wedge segments are;
• 3 a schematic view of the eccentric bearing area of the adjustment fitting according to the invention in a second view management form in which contours are formed in the wedge segments, with the drive means acting on them forming active points which are arranged even closer to the end faces of the wedge segments and further further in the direction of a respective outer surface of the wedge segments.

Both versions:

the 2 and 3 show the essential for the invention eccentric bearing area of an adjustment fitting 10 in each case in a schematic view. The basic configuration of the adjustment fitting 10 with its components mentioned in the preamble of claim 1 is described below with further use of the reference symbols DE 44 36 101 B4 described, since the basic structure of the adjustment fitting 10, as far as the components are concerned, is as already described in 1 described, is also the basis of this invention. The differences to DE 44 36 101 B4 will become clear in the following description.

In the schematic view of the eccentric bearing area in the 2 and 3 In contrast to the prior art, the adjusting fittings 10 according to the invention shown are formed with contours 28-1 on the drive means side in the wedge segments 24, which, in contrast to the prior art, lie in the area of the broad sides of the wedge segments 24, in particular near the broad end face 24BS of the wedge segments 24.

Together with the outer contours of the engaging drive means 22, which is designed in the manner of a driver, these drive means-side contours 28-1 in the wedge segments 24, which are designed as inner contours, form imaginary active points 31, 31', which act as drive points of the drive means 22, the drive points and thus the active points 31, 31' within the adjustment fitting 10 assume a certain predeterminable position.

As already explained, in contrast to the prior art, the respective at least one drive means 22 engages in the area of the broad sides of the two wedge segments 24, with a spring element 13 which is arranged separately from the drive means 22 and which, in contrast to the prior art, acts as an energy accumulator not the broad sides, but the narrow sides of the wedge segments 24 pulls together in the sense of influencing the radial play.

First embodiment:

The drive points and thus the points of action 31 of the drive means 22, according to 2 , are close to the wide end face 24BS and thus close to the end faces 26 of the wedge segments 24. The spring element 13 engages with its end regions near the narrow end face 24SS on the left and right in the left and right wedge segment 24 in the spring element-side contours 28-2, the are designed as inner contours, a.

Second embodiment:

In the second embodiment, the drive points of the drive means 22 and thus the points of action 31 'are, according to 3 , not only near the wide end face 24BS, but also, in contrast to the prior art, also near the outer surfaces 24A of the wedge segments 24. As in the first embodiment, the spring element 13 engages with its end regions near the narrow end face 24SS on the left and right the left or right wedge segment 24 into the contours 28-2 on the spring element side.

Both versions:

Both embodiments ensure an advantageous mode of operation, namely that the drive means 22, through the drive points forming the points of action 31, 31', form directions of force F31 or F31', which act in the circumferential direction of the adjustment fitting 10, but the directions of force are aligned in such a way that they have a lower Cause frictional force between the wedge segments 24 and the adjacent bearing ring 25.

The respective force of the force directions F31, F31' shown by the arrows in both embodiments acts near the end faces 26 depending on the direction of rotation of the adjustment fitting 10 in one direction or the other in the circumferential direction of the adjustment fitting 10, with the bearing ring 25 of the second fitting part 12 acting frictional forces between the wedge segments 24 and the bearing ring 25, in this close arrangement of the drive means 22 end of the wedge segments 24 and near the surfaces 26, compared to the prior art can be reduced.

The closer the points of action 31, 31' are arranged to the surfaces 26 of the end faces 24BS of the broad sides, compare 2 and 3 As measurements have shown, there is a reduction in the drive torque of the adjustment fitting 10 due to the reduction in frictional force between the surfaces of the contact area of the wedge segments 24 and the surface of the contact area of the surrounding bearing ring 25 of the second fitting part 12.

The further the action points 31, 31' are arranged towards the outer surface 24A of the wedge segments 24, compare 2 and 3 , done like that Measurements have further shown a further reduction in the drive torque of the adjustment fitting 10 by reducing the frictional force of the surfaces of the contact area of the wedge segments 24 in relation to the surface of the bearing ring 25 of the second fitting part 12 surrounding the wedge segments 24.

In this case, the forces F31' act in the drive points of the second embodiment [ 3 ] starting from the Y-axis at a second radius r2 further outwards in the circumferential direction than the forces F31 of the points of action 31 of the first embodiment [ 2 ] located at a first radius r1 from the Y-axis.

The points of action 31' [ 3 ] of the second embodiment are closer to the outer surfaces 24A of the wedge segments 24 than the action points 31 of the first embodiment, which are only the first radius r1 away from the Y-axis, starting from the Y-axis.

By relocating the drive points or active points 31′ outwards at a greater distance from the Y-axis, in a larger radius r2>r1, according to the second embodiment, compared to the first embodiment and compared to the prior art as a whole, an even further improved effect is achieved Arrangement of the components within the adjustment fitting 10 created. Here, the effective points 31' are further outwards than in the first embodiment, whereby the forces F31' act further outwards in the circumferential direction and the wedge segments 24 work with less friction during the adjustment of the adjustment fitting 10 relative to the bearing ring 25.

The forces F31' at the point of action 31' are in 3 marked with the force direction arrows F31'. The first angle α1 of the first embodiment, according to 2 forms in relation to the first dash-dotted reference line B1 and is identified by the force direction arrows F31 at the point of action 31, is greater (α1>α2) than the second angle α2, which is in accordance with 3 between the second dot-dash reference line B2 of the second embodiment. The points of action 31 ′ are thus moved closer to the surfaces 26 of the wedge segments 24 . In 3 the forces of the second embodiment are illustrated with the force direction arrows F31' at the point of action 31'. The closer the point of action 31' is to the surface 26 of the end face 24BS of the broad sides and the further the point of action 31' is arranged in the direction of the outer surface 24A of the wedge segments 24, the combination of effects results in a reduction in the drive torque of the adjustment fitting 10 due to the reduction in friction between the Surfaces of the contact areas of the wedge segments 24 and the surfaces of the contact areas of the bearing ring 25 surrounding the wedge segments 24 of the second fitting part 12.

This mode of action of reducing the frictional force is thus achieved through two points. First, the drive points and thus the points of action 31, 31' of the forces to be transmitted are formed close to the end faces 24BS of the broad sides of the wedge segments 24, at the end of the wedge segments 24, and secondly, the drive points or the points of action 31, 31'--as far as possible in the direction - i.e. located near the outer surfaces 24A of the wedge segments 24.

Overall, the position of the points of action 31, 31' and therefore the position of the drive points of the drive means 22 decides from which position the forces F31, F31' of the drive means 22 unfold at the beginning and in the course of the adjustment movement of the adjustment fitting 10 and in which position the points of action 31, 31' are located relative to the bearing ring 25 at the beginning and in the course of the adjustment movement of the adjustment fitting 10.

For the detailed implementation of the first embodiment:

In the arrangement shown 2 the drive means 22 has a central curved area which follows the outer contour of the collar line 19 of the first fitting part 11 with its inner surface. The outer contour of the drive means 22 has two short extensions 22-1K, which run in the radial direction in relation to the Y-axis of the axis of rotation of the adjustment fitting 10. The short extensions 22-1K are spaced apart from one another at a predeterminable angle β1, which is plotted between the auxiliary lines H1. The short extensions 22-1K engage in corresponding shorter indentations 32-1K of the wedge segments 24 in the wedge segments 24. In the short extensions 22-1K, the symmetrically opposite active points 31 are formed, each at the radial distance of the first radius r1 from the Y axis, in the opposite wedge segments 24, which lie on the dot-dash reference line B1. In the 2 the force directions F31 emanating from the points of action 31 are shown, which run orthogonally to the auxiliary lines H1 arranged radially with respect to the Y-axis. The force directions F31 run in the circumferential direction of the wedge segments 24, relative to the reference line B1 at the angle α1. This angle α1 can be changed by the action points 31 moving closer to the surfaces of the wedge segments 24, so to speak, being formed as far as possible at the ends of the wedge segments 24, as in the second embodiment based on the action points 31' in 3 indicates.

For the detailed implementation of the second embodiment:

In the arrangement shown 3 the drive means 22 also has a central curved area which follows the outer contour of the collar 19 with its inner surface. In contrast to the first embodiment, the outer contour of the drive means 22 has two long extensions 22 - 1L which run in the radial direction in relation to the axis Y of the axis of rotation of the adjustment fitting 10 . In addition, compared to the first embodiment, the long extensions 22-1L are at a smaller, predeterminable angle β2 (β1>β2), which is plotted between the auxiliary lines H2, away from one another. The long extensions 22-1L engage in associated depressions 32-1L in the wedge segments 24 which are longer than in the first embodiment. In the long extensions 22-1L, the symmetrically opposite active points 31' are formed, each at the radial distance of the second radius r2 from the Y axis, in the opposite wedge segments 24, which now lie on the dot-dash reference line B2. In the 3 the directions of force F31' emanating from the points of action 31' are shown, which run orthogonally to the auxiliary lines H2 arranged radially with respect to the Y-axis. The directions of force F31' run in the circumferential direction of the wedge segments 24, relative to the reference line B2, at an angle α2 which is smaller than the angle α1 (α2<α1).

Changing the position of the effective points 31, 31' according to the first and second embodiment F31' makes it clear that, compared to the prior art, the direction of the force F31, F31', which acts on the respective wedge segment 24 and the adjacent component, the bearing ring 25 is transmitted, can be changed in favor of a low drive torque by reducing the friction of the surfaces of the wedge segments 24 and the bearing ring 25 that are in contact with one another, in that the drive points or the effective points 31, 31' of the at least one drive means 22 are arranged or formed close to the surfaces 26 of the wedge segments 24 and/or in that the drive points or the effective points 31, 31′ of the at least one drive means 22 are arranged or formed near the outer surfaces 24A of the wedge segments 24.

Furthermore, the contours 28-2 on the spring element side in the wedge segments 24 near the narrow end faces of the wedge segments 24SS are also designed as groove-like depressions 32, so that the ends of the spring element 13 can be easily fastened in these depressions 32 in the wedge segments 24, in particular can be hooked in.

The adjustment fitting 10 is designed with a cover disc, not shown, which has at least the drive means 22 or the drive means 22 and a hub 21, with the drive means 22 being the driver.

Insofar as a cover disk is designed with a driver and a hub 21, the cover disk has a socket-like receptacle in its center, which is available for a torque-transmitting transmission element.

In a preferred embodiment, the cover disc is connected in one piece to the driver arranged at a radial distance from the hub 21 . In a further preferred embodiment, the cover plate overlaps the gear area of the pivotable second fitting part 12.

The hub 21 of the driver has a continuous receptacle in its center, which is designed as a conical bore and has a conical surface that widens slightly towards the inside of the seat.

The driver is provided with an annular groove on its hub region which protrudes in the axial direction in relation to the cover disk. Locking fingers can be clipped into this annular groove, which are part of a drive member which is connected to a transmission rod (also not shown) in a torque-transmitting manner.

The drive element is, for example, a handwheel, on the hub of which the locking fingers are located, which can be injection-molded in one piece from plastic. The hub itself has a driver bore which is profiled to match the transmission rod and is used for rotary driving, while the axial position of the handwheel is secured by the locking fingers.

As explained, the cover disc can be integrally formed on the hub 21 .

The cover disc is advantageously designed in two parts, since the hub body is to be made of a hard material for stability reasons, while the upper part of the cover disc should advantageously consist of a softer material for better sealing, to avoid noise and to avoid an increased operating torque.

Reference List

10

adjustable fitting

11

fitting part, fixed

12

Fitting part, swivelling

13

spring element

14

eccentric means

15

spur gear

16

external teeth

17

sprocket

18

internal teeth

19

collar pull

20

driver

21

hub

22

drive means

22-1K

short extension

22-1L

long process

24

wedge segment

24SS

narrow face of the wedge segment

24BS

wide face of the wedge segment

24A

outer surface

24I

Inner surface

25

bearing ring

26

surfaces

27

Spring leg of a spring element

28-1

drive center-side contour in the wedge segment

28-2

spring element-side contours in the wedge segment

29

effective surface lying in a radial plane

Q29

Direction of force emanating from the radial effective area

31

point of action

F31

direction of force emanating from 31

31'

point of action

F31'

direction of force emanating from 31'

32

groove/depression

32-1K

short deepening

32-1L

long deepening

α1, α2

angle

r1, r2

Distance

e

eccentricity

Y

Axis of the adjustment fitting

B1

reference line

B2

reference line

H1

auxiliary line

H2

auxiliary line

Claims (7)

Adjustable fitting (10), in particular for motor vehicle seats, in which a fixed fitting part (11) assigned to the seat part and an adjustable fitting part (12) assigned to the backrest have an adjustment and locking device which determines the position of the two fitting parts (11, 12) relative to one another Gears are connected to one another, the fitting parts (11, 12) of which are mounted eccentrically in the plane of action of their teeth (16, 18) under the influence of at least one drive means (22) which can be rotated about a pivot axis (Y), characterized in that at least one drive means (22) with a force transmitted from at least one drive point to wedge segments (24) at at least one effective point (31, 31') in the area of the broad sides of the two wedge segments (24), which is in each case close to a surface (26) of the wedge segments (24) lies, acts in such a way that the wedge segments (24) bear more strongly in a direction of force (F31, F31') lying in the circumferential direction of the adjustment fitting (10). are driven, a spring element (13) which is arranged separately from the drive means (22) and which, as an energy accumulator, pulls the narrow sides of the wedge segments (24) together in the sense of influencing the radial play, is formed. adjustment fitting claim 1 , characterized in that in the wedge segments (24) in the area of the broad sides near the broad end faces (24BS) drive means-side contours (28-1) are formed. adjustment fitting claim 2 , characterized in that the contours (28-1) on the drive means side are inner contours which, together with the outer contours of the drive means (22), which engages in the inner contours and is designed in the manner of a driver, form imaginary points of action (31, 31'), which act as drive points of the drive means (22). adjustment fitting claim 3 , characterized in that the drive points or active points (31, 31') of the drive means (22) are arranged at a predeterminable distance (r1, r2) from the adjustment axis (Y) of the adjustment fitting (10), the distance (r1, r2 ) via the adjustment of a depth of a depression (32-1K, 32-1L) forming the inner contour in the wedge segments (24) or correspondingly via the length of the extensions (22-1K, 22-1L) of the drive means (22 ) made men will engage in the corresponding recess (32-1K, 32-1L). adjustment fitting claim 1 , characterized in that the spring element (13) with its end regions close to the narrow end face (24SS) of the wedge segments (24) on the left and right in the left and right wedge segment (24) in contours (28-2) on the spring element side, which as inner contours are trained, intervenes. adjustment fitting claim 5 , characterized in that contours (28-2) on the spring element side are formed in the wedge segments (24) as groove-like depressions (32), whereby the ends of the spring element (13) can be fastened, in particular suspended, in these depressions (32). adjustment fitting claim 1 , characterized in that the drive means (22) is a driver which is designed as a cover disc with a hub (21) which has a central, torque-transmitting receptacle, the cover disc being in one piece with the driver arranged at a radial distance from the hub (21). is connected, the cover plate overlapping the gear area of the two fitting parts (11, 12) on the outside.

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